Presses



1962 G. SCHAMING 3,049,029

PRESSES Filed Sept. 9, 1958 5 Sheets-Sheet 1 J MWI FIG-l Aug. 14, 1962 G. SCHAMING PRESSES 5 Sheets-Sheet 2 Filed Sept. 9, 1958 4, 1962 G. SCHAMING 3,049,029

PRESSES Fi1ed p 9, 1958 5 Sheets-Sheet 4 7 liad Fla. 8

5] 53 Q M? 5 a j/M WI Aug. 14, 1962 G. SCHAMING 3,049,029

PRESSEIS Filed Sept. 9, 1958 5 Sheets-Sheet 5 3,049,029 PRESSES Guillaume Schaming, Le Perreux, France, assignor to Societe Anonyme Schostal, Vaduz, Liechtenstein, a society of Liechtenstein Filed Sept. 9, 1958, Ser. No. 759,878 Claims priority, application France Sept. 13, 1957 Claims. (Cl. 74-785) The present invention refers to mechanically operated presses comprising a slide-block actuated by a connecting rod driven by an eccentric or crank shaft.

The invention comprises improvements in such presses, especially for improving their operation, by rendering it more certain and more flexible.

According to the invention, the eccentric or crank shaft is secured to a plate on which there are rotatably mounted planet pinions engaging with a stationary outer gear ring and with a central pinion secured to the driving member of the press. Thus, with a driving member rotating at a relatively high speed, there can be obtained a sufficiently low speed of the eccentric or crank shaft. Such an arrangement permits of driving the press by means of an electric motor, and reducing its speed simply by a normal belt-pulley transmission, without having to use mechanical reduction gearing of the usual type, with a small pinion keyed on the motor shaft and a large-diameter gear wheel keyed on the driving shaft of the press. Furthermore, by reason of the use of a plurality of symmetrically disposed planet pinions, a balanced drive is obtained, exerted at a plurality of points, instead of at one single point as in the usual arrangements.

In accordance with another feature of the invention, the connection between the driving member of the press and the source of power is effected by means of a friction clutch controlled mechanically, electromagnetically or by pressure fluid, which permits a slipping action in the case of an excessive force exerted upon the press.

The invention also comprises an arrangement whereby the pin or gudgeon coupling the sliding block of the press with the connecting rod is mounted eccentrically at its two ends, so that the eccentricity can be varied and consequently the position of the slide block in relation to the lower table can be adjusted for the working stroke of the tools operated by the press. This adjustment can be effected micrometrically by means of a worm actuated from the exterior and in engagement with a toothed ring provided on the eccentric pin or gudgeon coupling the connecting rod to the slide block.

For the guidance of the slide block, detachable slideways of considerable length are used, which increase the bearing surfaces of the guides. These slide-ways may be removable, as by mounting them in dovetailed grooves on the sides of the slide block.

The invention enables the eccentric or crank shaft to be made in one piece, the connecting rod being also made in one piece or provided with a divided bearing cap at one end.

Other objects and advantages of the invention will hereinafter appear from the following description of suitable embodiments given simply by way of example, with reference to the accompanying drawings, wherein:

FIG. 1 is an elevation of the press;

FIG. 2 is an enlarged detail of the device for driving the press by means of an electro-magnetically controlled clutch;

FIG. 3 is a section along the line III-III in FIG. 1;

FIG. 4 is an enlarged detail of a device for adjusting the position of the slide block in relation to the table of the press;

FIG. 5 is an enlarged detail in section of another embodiment of the device for driving the press by means of a clutch controlled by pressure fluid;

3,649,929 Patented Aug. 14, 1962 FIG. 6 is a section showing the arrangement for the supply of fluid in FIG. 5;

FIGS. 7 and 8 are enlarged details respectively in longitudinal section and in section along the line VIII--VIII of FIG. 7, showing means for varying the stroke of the extractor;

FIGS. 9 to 11 are part sectional details of a brake for the press.

As represented in FIGS. 1 and 3, the press comprises a frame 1, a slide block 2, a shaft 3 having an eccentric or crank-throw 4, and a connecting rod 5 mounted on the eccentric, the other end of which is attached to a pin or gudgeon 6 for connection with the slide block 2. It also comprises a table 7 provided with an extractor device 8'.

The press is driven, for example by an electric motor (not shown) by means of V-belts passing over a grooved pulley 9, the shaft 3 being driven through a clutch, which may be controlled mechanically, electro-magnetically or by fluid under pressure.

In the embodiment represented in FIG. 2, the press is driven through a clutch with electro-magnetic control.

In this embodiment, the pulley 9, concentric with the shaft 3, is secured to a plate .10 inside which there is provided a magnet winding 11. Beside this plate there is mounted a ring 12, connected thereto by means of rods 13 slidable against springs 14, in such a way that, while rotating with the plate 10, the ring 12 can move axially in relation thereto. The plate 10 and the ring 12 are made of magnetic material, forming an electro-magnet energized by the winding 11. In the air-gap of this electro-magnet there is provided a disc 15 fitted with linings 16 of a material having a high coefficient of friction. This disc is connected by a spider or plate 19 to a pinion 17 rotatably mounted on the shaft 3. The supply of electric current to the winding 11 is effected by means of brushes 18a contacting with conductor rings 18 carried by the pulley 9 and connected to the winding 11.

When the electromagnet 10, 12 is energized, the movable ring or armature 12 is attracted towards the plate 10, and the disc 15 is frictionally connected to the pulley 9, the movement of the latter being thus transmitted to the pinion 17.

This pinion 17 engages with planet pinions 20, for example four in number and spaced at apart. These pinions rotate on spindles 21 carried by a plate 22 keyed to the shaft 3, and they also engage with a stationary outer gear ring 23 secured to the frame 1 of the press.

Thus the shaft 3 is driven for operation of the crank 4 through the intermediary of the planet pinions 21, the gear-ratio between said pinions and the central pinion 17 being selected in such a way that a suitable reduction of speed is obtained.

In the embodiment represented in FIGS. 5 and 6, the press is driven through a clutch with pressure-fluid control. The pulley 9 is here shown secured to a plate 30 concentric with the shaft 3 and on which there is fixed an annular plate 31, also concentric with the shaft. As in the preceding embodiment, the means for driving the press comprises a toothed pinion 17 rotatably mounted on the shaft 3, and planet pinions 20 rotatable on spindle 21 carried by a plate 22 secured to the shaft 3, these planet pinions engaging with an outer toothed ring 23 secured to the frame of the press.

In the annular plate 31, there is mounted in fluidtight manner an elastic diaphragm 32, facing which there is provided an annular plate 33 adapted to press against a ring 34 which is secured to rods 35 slidable in the plate 30 against the action of springs 36.

In the space between the ring 34 and the internal face of the plate 30, there is provided a disc 40 which is secured to the pinion 17. Linings 37 of a material having a high coeflicient of friction are provided between the disc 40 and the plate 30 and ring 34 on opposite sides thereof.

When the press is idle, the springs 36 cause the ring 34 to move away from the plate 30, the clutch being free. To operate the shaft 3 of the press, pressure fluid is admitted between the plate 31 and the diaphragm 32; the latter therefore presses back the parts 33, 34, so that the disc 44) is driven by the friction linings 37. The central pinion 17 is thus driven and the press operates as in the preceding example. The bearings provided upon the shaft 3 and the parts driven by the disc 40 are arranged in such a way as to permit the slight longitudinal play necessary for the clutch engagement and disengagement.

As represented in FIG. 6, pressure fluid from a distributor working in timed relation with the press, is delivered through a conduit 41 opening into a rotary joint member 42 in axial relation to the shaft 3 of the press.

This joint 42 is connected by conduits 43, 44, leading through radial grooves 45 provided on the plate 31 to a circular channel 46. The conduits 43, 44 may be arranged in threes, disposed at 120 apart, in order to obtain a good distribution of the pressure fluid and properly balanced action.

The pin or gudgeon 6, by which the connecting rod is attached to the slide block 2 of the press, is preferably made eccentric at its two ends. Variation of this eccentricity is effected by means of a worm 25 mounted on the slide block and capable of being controlled from the exterior by means of a square end 26, as seen in FIG. 4. This tangential worm 25 engages with a toothed ring 27 provided on the pin 6. By turning the pin 6, the eccentricity can be varied, whereby the limiting position of the slide block in relation to the table 7 can be adjusted. Means may be provided for locking the pin in the position which has been adjusted in this way.

In order to improve the guiding of the slide block 2, there may be attached on the uprights 23 parallel slideways 29 of considerable length, these slide-ways being preferably mounted on dovetails and secured by any appropriate means.

It will be observed that the crank shaft 3 is in one single piece with its eccentric or crank throw 4. The same applies to the connecting rod 5, which may however be fitted with a divided bearing at one end.

The press can be provided with means for extraction of the work-pieces, having a stroke continuously variable by shifting the fulcrum of the actuating lever, such an arrangement being represented in FIGS. 7 and 8. The extractor 8, which may be multiple or may be arranged as a movable pressure table, is operated by means of links 50 articulated at 50a on a lever 51. A control member 59 acts through a joint 52 and an articulation 53 upon one end of this lever, the other end of which is mounted on a fulcrum 54 which is movable in relation to the frame of the press. In the form of embodiment repre sented, the lever 51 formed of two side-pieces having slotted engagement with a die or fulcrum 54 adjustable along slideways 55, the die forming a nut for a screw 56 which can be operated from the exterior.

It will be seen that by turning this screw, the die or nut is shifted bodily along the slideways, and that consequently the fulcrum position of the lever 51 varies, thereby allowing for longer or shorter stroke of the extractor.

The press may be provided with a braking device mounted at the end of the crank shaft, and adapted for actuation by any appropriate means, for example electropneumatic.

In FIGS. 9 to 11, there are represented three radial sections, taken at different angular positions, of a disc braking device mounted on the crank shaft 3 on the side of the press opposite to that Where the driving pulley is mounted.

On the shaft 3, there is keyed a sleeve 60, on which there is fixed by screws 61 a disc 62. Furthermore, a ring 64 is mounted by screws 63 on the press frame 1.

Engaging in grooves formed on the outer edge of this ring 64, and parallel to its axis, there are slidably mounted two plates 65, 66 carrying linings 67, 68 of a material having a high coeflicient of friction. As seen in FIG. 9, these two plates have aligned holes through which there pass members 69 each having a shoulder 70 and each engaged internally by a screw-threaded rod 71, also having a shoulder 72. A compression spring 73 bears at one end on the inner plate 66 and at the other end on the shoulder 72 of the rod 71, bringing the two plates towards one another and thereby effecting a braking action upon the central disc 62 secured to the shaft 3.

In a chamber 85 inside the ring 64, as seen in FIG. 10, there are provided two cheek plates 74, 75, concentric with the axis of the shaft 3, and movable in relation to one another. These two cheek plates are mounted on a plate 76 fixed on the ring 64, being assembled thereto by means of rings 77, 78 secured to the plate 76, and on which the cheek plates 74, can slide.

The part 76a of the plate 76 comprises a channel 79 in communication through a joint member 80 and a pipe 81 with a source of pressure fluid. The channel 79 opens out through ports 82 into the space included between the cheek plates 74, 75.

The check plate 74 contacts with gudgeons 83 secured to the plate 65. The cheek plate 75 is secured to gudgeons 84 fast with the plates 66, as shown in FIG. 11.

When the press is in operation, pressure fluid is intro duced through the pipe 81 into the space between the cheek plates 74, 75. The result is a lateral pressure between these two cheek plates which pushes them apart and consequently thrusts the plate 65 outwards and draws the plate 66 inwards, against the action of the spring 73. Thus there is no braking of the press while in operation, but breaking is exerted as soon as the supply of the pressure fluid stops.

The press may be provided with cams for ensuring the control of its various operations, and with the usual accessories.

The invention is not limited to the forms of embodiment described, but can be carried out in accordance with various modifications within the scope of the appended claims.

What I claim is:

l. A mechanically operated press comprising, in combination, a press frame; a slide reciprocable in said press frame; a drive shaft turnably mounted in said press frame; means operatively connected to said shaft and said slide for reciprocating said slide upon turning of said shaft; a combined pulley and flywheel member turnably mounted on said shaft; a sun gear turnably mounted on said shaft; a plurality of planet gears uniformly distributed about said sun gear and in meshing engagement therewith; support means for supporting said planet gears and being fixed to said shaft for rotation therewith; an outer gear ring surrounding said planet gears in meshing engagement with the latter, said outer gear ring being fixedly carried by said press frame; and clutch means interposed between said combined pulley and flywheel member and said sun gear for connecting and disconnecting said member to and from said sun gear.

2. A mechanically operated press comprising, in combination, a press frame; a slide reciprooable in said press frame; a drive shaft turnably mounted in said press frame; means operatively connected to said shaft and said slide for reciprocating said slide upon turning of said shaft; a combined pulley and flywheel member turnably mounted on said shaft, said combined pulley and flywheel member having an outer rim portion and a flange portion extending transverse to said outer rim portion from one side of the latter, the inner surfaces of said portions defining a substantially cylindrical hollow space in said member; a sun gear turnably mounted on said shaft; a plurality of planet gears uniformly distributed about said sun gear and in meshing engagement therewith; support means for supporting said planet gears and being fixed to said shaft for rotation therewith; an outer gear ring surrounding said planet gears in meshing engagement with the latter, said outer gear ring being fixedly carried by said press frame; and clutch means interposed between said combined pulley and flywheel member and said sun gear for connecting and disconnecting said member to and from said sun gear, said gears and clutch means being located in said hollow space of said combined pulley and flywheel member.

3. For use in a machine such as a mechanically operated press or the like, in combination, a stationary frame; a rotary drive shaft carried by said frame; a sun gear coaxially surrounding and freely turnable with respect to said shaft; an outer ring gear having inner teeth directed toward said sun gear, said ring gear coaxially surrounding and being spaced from said sun gear and said ring gear being fixedly carried by said stationary frame so that said ring gear also is stationary; a plurality of planetary gears located between and meshing with said sun gear and ring gear; support means supporting each of said planetary gears for free rotary movement about its axis, said support means being fixed to said drive shaft so that movement of the planetary gears about the axis of said drive shaft transmits a drive thereto; a rotary driving pulley coaxial with said drive shaft and located adjacent said gears; and friction clutch means operatively connected to said pulley and sun gear for transmitting a drive from said pulley to said sun gear when said friction clutch means is engaged, whereby said drive shaft will be driven from said pulley at a substantially lower speed than said pulley when said clutch means is engaged and whereby said clutch means can slip even when engaged to prevent damage to other elements.

4. For use in a machine as recited in claim 3, said frame having a side surface beyond which said drive shaft extends and said ring gear being fixed to and located adjacent said side surface of said frame, said support means being located between said planetary gears and said side surface of said frame and said clutch means being located adjacent to said sun gear and planetary gears at the side of the latter opposite from said support means.

5. For use in a machine as recited in claim 4, said pulley also acting as a flywheel and being freely turnable on a free end portion of said shaft at the part thereof extending beyond said side surface of said frame, said pulley being hollow, having a free annular edge portion located adjacent said side surface of said frame and all of said gearing, said support means, and said clutch means being housed within said hollow pulley.

References Cited in the file of this patent UNITED STATES PATENTS 311,255 Pedersen Jan. 27, 1885 1,675,669 Snyder July 3, 1928 2,151,890 Bobst Mar. 28, 1939 2,280,849 Pocock Apr. 28, 1942 2,523,393 Rhodes Sept. 26, 1950 2,553,521 Reitberger May 15, 1951 2,577,641 Wissman Dec. 4, 1951 2,608,253 Battles Aug. 26, 1952 2,755,147 Ernst July 17, 1956 2,781,879 Ebersold Feb. 19, 1957 2,818,798 Deykin Jan. 7, 1958 

